|Publication number||US6682327 B2|
|Application number||US 10/223,143|
|Publication date||27 Jan 2004|
|Filing date||19 Aug 2002|
|Priority date||26 Feb 2001|
|Also published as||US20020192094|
|Publication number||10223143, 223143, US 6682327 B2, US 6682327B2, US-B2-6682327, US6682327 B2, US6682327B2|
|Inventors||Tracy L. Milliff, John R. Williams|
|Original Assignee||Scroll Technologies|
|Export Citation||BiBTeX, EndNote, RefMan|
|Patent Citations (3), Referenced by (30), Classifications (6), Legal Events (4)|
|External Links: USPTO, USPTO Assignment, Espacenet|
This application is a continuation-in-part of Ser. No. 09/793,369 filed Feb. 26, 2001, U.S. Pat. No. 6,488,489, and Ser. No. 09/872,972, filed Jun. 1, 2001, U.S. Pat. No. 6,560,868.
This invention relates to a method wherein the components adjacent the top and bottom of a scroll compressor are all aligned with regard to a common reference such that total alignment of the components can be more easily and accurately achieved.
Scroll compressors are becoming widely utilized in refrigerant compression applications. In a scroll compressor, first and second scroll members each include a base and a generally spiral wrap extending from the base. The wraps interfit to define compression chambers. A shaft is operably connected to one of the scroll members to cause that scroll member to orbit relative to the other. As the two scroll members orbit, compression chambers defined between the wraps of the two scroll members decrease in volume, compressing an entrapped refrigerant.
Historically, scroll compressors are mounted in a sealed housing. The housing includes a center shell and upper and lower end caps. The shaft which drives the orbiting scroll member is typically driven by an electric motor mounted within the center shell. The shaft extends along a rotational axis, and is operably connected to the orbiting scroll to cause orbiting movement of the orbiting scroll. Typically, the shaft is mounted in bearings adjacent upper and lower positions. The upper bearing is mounted within a crankcase, which supports the orbiting scroll member. The lower bearing is typically on an opposed side of the motor from the scroll members. Historically, a bearing support has extended radially inwardly from the center shell to support the lower end of the bearing.
More recently it has been proposed to mount the lower bearing in the scroll compressor on the lower end cap. Thus, in prior U.S. patent application Ser. No. 09/376,915, filed Aug. 18, 1999, U.S. Pat. No. 6,247,909 and entitled “BEARING ASSEMBLY FOR SEALED COMPRESSOR”, and further in a co-pending application entitled “LOWER END CAP FOR SCROLL COMPRESSOR” filed on Jun. 1, 2001 and assigned Ser. No. 09/872,972, U.S. Pat. No. 6,560,868, lower end cap structure for mounting a bearing has been disclosed.
Further, it has recently been proposed to force fit the crankcase into the center shell such that the position of the crankcase is ideally located relative to the center shell. Such structure has been disclosed in co-pending application Ser. No. 09/176,576, filed Oct. 21, 1998 and entitled “FORCE-FIT SCROLL COMPRESSOR ASSEMBLY” and now assigned U.S. Pat. No. 6,193,484.
However, the two ideas have never been proposed to be combined.
In the disclosed embodiment of this invention, the center shell is utilized as a point of reference to ideally position the lower bearing through the mount of a lower end cap, and the crankcase both at a location ideally determined and positioned by the common reference. In a preferred embodiment, the common reference is provided by the center shell. The center shell is machined to have carefully controlled end surfaces that are both perpendicular to the center axis of the center shell, and which are ideally close to being cylindrical. The initial shell formation can be slightly out of round (i.e., on the order of 1.0 mm), as it will be brought to complete roundness by the computer cut surfaces of both the crankcase and the lower end cap, and as will be explained below.
The lower end cap is machined such that it has mount surfaces which are both perpendicular to the lower bearing bore and a set radial spacing away from the axis of the lower bearing. When this lower end cap is mounted within this center shell, the bearing is thus ideally located relative to the center axis of the center shell.
In a further embodiment, the unshaped structure which provides the outer surface for machining to ensure the lower bearing bore is true, is provided as a separate part welded to the lower shell. This simplifies the formulation of the lower shell blank.
Further, the crankcase is machined to have an idealized outer cylindrical surface, and a flat end face which abuts the end face of the center shell. When this crankcase is mounted in this center shell along with the lower end cap, it is assured that the crankcase and the lower end cap are both mounted at a proper orientation relative to each other. Since both the end cap and the crankcase are separately machined on their own to ensure that the axis of the bearing for the shaft that they each carry are true to the outer periphery of the individual component, it is also ensured that the two bearings are thus ideally located relative to each other. Once these two bearing mounts for the shaft are ideally determined, the other components of the scroll compressor come together easily and at assured aligned position.
Thus, the present invention provides a simplified method of ideally locating components within a scroll compressor such that it is assured they are properly located.
These and other features of the present invention can be best understood from the following specification and drawings, the following of which is a brief description.
FIG. 1 is a cross-sectional view through the inventive scroll compressor.
FIG. 2A is an enlarged view of circle portion 2A from FIG. 1.
FIG. 2B is an enlarged view of circle portion 2B from FIG. 1.
FIG. 3 schematically shows the formation of a shell component.
FIG. 4A shows the first step in assembly.
FIG. 4B shows a subsequent step.
FIG. 4C shows yet another step.
FIG. 4D shows yet another step.
FIG. 5A is a top view of an end cap.
FIG. 5B shows an enlarged portion of one location on the FIG. 5A end cap.
FIG. 6 shows another feature of an inventive bearing.
FIG. 7 shows a feature of the FIG. 6 embodiment.
FIG. 8A shows a further embodiment.
FIG. 8B shows an alternative to the FIG. 8A embodiment.
FIG. 9A shows another embodiment.
FIG. 9B shows an alternative to the FIG. 9A embodiment.
FIG. 1 illustrates a scroll compressor 20 incorporating an orbiting scroll 22 and a non-orbiting scroll 24. A driveshaft 26 is driven by a motor stator 28 through rotor 30. The driveshaft is operatively connected to cause orbiting movement of the orbiting scroll 22. The lower bearing 32 is mounted on an end cap 34. A lower end 33 of the shaft 26 engages the lower bearing 32. The end cap 34 has circumferentially spaced u-shaped portions 36 positioned radially inward of a lower end 39 of a center shell 40. The lower end 38 of the center shell 40 has an axial end surface 39 which abuts a surface on the lower shell 34, as will be explained below.
An inner periphery 41 of the center shell is formed to be close to an idealized cylinder to facilitate alignment, as will be explained below. An upper end cap 42 is secured to the center shell 40. A crankcase 44 supports the orbiting scroll 22, as known. An outer peripheral portion 46 of the crankcase 44 has an outer surface 47 which is force fit within the center shell 40.
A bearing 48 is mounted within the crankcase 44 and supports an upper end of the shaft 26. A radially outwardly extending lip 50 of the crankcase 44 abuts an end 52 of the housing 40. As will be explained below, the combination of the force fit crankcase and the bearing mounted on the lower end plate provides assurance that the bearings 32 and 48 are located on an axis which is common by setting both bearings based upon a common reference.
As shown in FIG. 2A, the crankcase 44 has its outer periphery 47 force fit within the inner periphery 41 of the center shell 40. The radially outwardly extending flange 50 abuts the end face 52.
The downwardly facing surface 90 of the flange 50 is machined to be perpendicular to the center axis of the crankcase 47. Moreover, the outer periphery 47 of the crankcase 44 is also machined to be concentric with the bearing mount 48. Thus, by known computer control methods, Applicant ensures that the bore for the bearing 48 is concentric and ideally centered with the outer surface 47 and perpendicular to flange surface 90. It should be understood that the surface 47 may have some discontinuities, however, it is generally cylindrical, and concentric with the center axis of the bearing 48. Details of the preferred crankcase can be determined from U.S. Pat. No. 6,193,484.
Now, when the crankcase is mounted within the center shell 40 as is shown in FIG. 2A, due to the surface 90 abutting surface 52, and due to the force fit 47, one can be assured that the center axis of the bearing 48 is parallel and concentric with the interior axis of the center shell 40.
At the same time, a similar end face 54 is formed on the lower end plate 34. The axial end 39 of the lower end 38 of the center shell housing abuts the surface 54. As with the crankcase, this ensures that the lower end cap 34 is properly orientated within the center shell 40. Moreover, the outer periphery 91 of the portions 36 are sized to provide at least a slight force fit within the center shell 40. Again, this ensures that the orientation of the lower end cap 34 within the center shell 40 is idealized and true.
The center axis of the bearing 32 is preferably cut, as will be explained below, such that it is concentric with the outer periphery of the sections 36 and perpendicular to surface 39. This ensures that the bearing axis for bearing 32 is also based upon the center axis of the inner periphery 41 of the center shell 40. By utilizing these two techniques, applicant thus ensures the bearing 48 is centered on and parallel to an axis which is determined based upon the same point of reference as the axis for the bearing 32. Applicant thus ensures the bearings are more likely aligned than has been the case in the prior art.
FIG. 3 shows a machining operation 10 highly schematically. A shell preform 12 which becomes center shell 40 is initially formed into a generally cylindrical shell by rolling a portion of steel and then welding that steel into the perform and expanding from the inner diameter. An expanding mandrel 16 extends into the inner periphery of the shell 12 and ensures the inner periphery turns between centers of the lathe. The mandrel then brings the shell 12 to a pair of opposed machining lathes 14 which cut the end surfaces on the center shell. The operation for machining the shell is as known, and is within the skill of a worker in this art. The shell preform is thus formed into the center shell 40, and as shown in FIG. 4A, the end surfaces 39 and 52 both define flat surfaces which are computer controlled to be quite close to being true flat parallel planes perpendicular to inner axis. Moreover, the inner periphery 41 is extremely close to being a true cylindrical bore. As mentioned above, the inner periphery 41 can be slightly out of round at this point, as the crankcase and lower end cap surfaces will bring it to being true once inserted.
In a first step of assembling the scroll compressor, the stator 28 is initially placed within the center shell, as shown in FIG. 4A. The center shell may be heated to receive the stator, and then may then cool to secure itself onto the stator. Moreover, electrical connections are preferably made during the mounting of the stator, and as disclosed in co-pending U.S. patent application Ser. No. 09/415,122, filed on Oct. 8, 1999, U.S. Pat. No. 6,244,837, and entitled “DEFORMED COMPRESSOR MOTOR WINDING TO ACCOMMODATE COMPONENTS”.
As shown in FIG. 4B, the next step is to then force the center shell 40 downwardly onto the lower end cap 34. As described above, the lower end 38 of the center shell 40 provides a force fit onto the portions 36, such that at this point the bearing 32 has its center axis ideally centered relative to the center axis of the housing shell 40. At this time, the center shell may be tack welded to the lower end cap 34 to secure the two together for subsequent processing until final girth weld.
The next step is to mount the rotor 30 and shaft 26 within the bearing 32 and within the stator 28, as shown in FIG. 4C.
The next step is to force the crankcase 44 into the center shell 40. With this forced movement, the flange 50 is brought against the end 52. At this point, and since the bearing bore 48 has been previously cut to be a true concentric bore relative to the outer periphery 47 of the crankcase 44, it can be ensured that the bearings 48 and 32 are both centered on an axis cut relative to a common reference, the center axis of the center shell 40.
The components of the orbiting scroll and the non-orbiting scroll, including all the anti-rotation couplings, seals, etc., as are known are then placed within the compressor. The end cap 42 is then brought downwardly and the components are forced together and the upper end cap is tack welded. At that point, the end caps are welded to the center shell, securing the entire assembly.
FIG. 5A shows the lower end cap 34, with the bearing 32. As can be appreciated, the u-shaped surfaces 36 are circumferentially spaced. The outer periphery 91 of these components is cut such that this outer periphery is true and concentric to the central axis X of the bearing 32. As is explained in greater detail in co-pending U.S. patent application Ser. No. 09/376,915, filed Aug. 18, 1999, U.S. Pat. No. 6,247,909, and entitled “BEARING ASSEMBLY FOR SEALED COMPRESSOR” this is ensured by cutting the center X of the bearing to be concentric with the outer surface 91 of the portions 39. FIG. 5B shows another view of the outer surface 91 in the portion 36.
In sum, by ensuring the centers of the bearings 32 and 48 are both cut and measured by computer controlled equipment to be concentric with a common reference Applicant ensures the two bearings are ideally located and aligned relative to each other. The present invention thus improves greatly upon the prior art.
FIG. 6 shows a bearing embodiment 300 wherein the bearing hub has an upper end 302 which is tapered laterally inwardly from a lower end 304. When the bearing body 310, as shown in FIG. 7, is inserted, the upper end is bent back as shown at 312 relative to the lower end 314. In the prior art, when the bearing was inserted, it bent the unsupported upper end radially outwardly, and resulted in the free end of the hub being bent outwardly, rather than being a cylindrical surface. Thus, this reverse tapering provides benefits.
Essentially, the computer cut concentric outer peripheral surfaces on the crankcase and the lower end cap ensure that the bearing bores are each equally spaced radially from the inner periphery of the center shell. At the same time, the flat surfaces ensure that the crankcase and lower end cap will be parallel to each other, such that the axes of their bearing bores will be concentric and parallel also.
A further embodiment 400 is shown in FIG. 8A in which weld ring 401 is welded to the lower shell 402 to provide the outer surfaces which are machined as in the above embodiments to be concentric and peripheral with the bearing bore. As shown in FIG. 8B, several ring segments 405 could replace the ring 401.
In yet another embodiment shown in FIG. 9A, the bearing mount 500 extends outwardly to provide the outer surface 502. The surfaces 502 and 506 are machined to be concentric and peripheral, thus ensuring the alignment as mentioned above. As shown in FIG. 9B, several spokes 508 could extend to the outer shell to provide the surface 502.
Although a preferred embodiment of this invention has been disclosed, a worker in this art would recognize that modifications may come within the scope of this invention. For that reason the following claims should be studied to determine the true scope and content of this invention.
|Cited Patent||Filing date||Publication date||Applicant||Title|
|US5374166 *||4 Jan 1994||20 Dec 1994||Sanden Corporation||Motor driven fluid compressor within hermetic housing|
|US5382143 *||24 May 1994||17 Jan 1995||Mitsubishi Denki Kabushiki Kaisha||Scroll type compressor having a thrust plate in a frame recess|
|US6488489 *||26 Feb 2001||3 Dec 2002||Scroll Technologies||Method of aligning scroll compressor components|
|Citing Patent||Filing date||Publication date||Applicant||Title|
|US7766628 *||13 Apr 2006||3 Aug 2010||Scroll Technologies||Sealed compressor with structure on lower housing shell to assist weld placement|
|US7878775 *||17 Jan 2008||1 Feb 2011||Bitzer Kuhlmaschinenbau Gmbh||Scroll compressor with housing shell location|
|US7878780||17 Jan 2008||1 Feb 2011||Bitzer Kuhlmaschinenbau Gmbh||Scroll compressor suction flow path and bearing arrangement features|
|US7918658||17 Jan 2008||5 Apr 2011||Bitzer Scroll Inc.||Non symmetrical key coupling contact and scroll compressor having same|
|US7963753||17 Jan 2008||21 Jun 2011||Bitzer Kuhlmaschinenbau Gmbh||Scroll compressor bodies with scroll tip seals and extended thrust region|
|US7967581||17 Jan 2008||28 Jun 2011||Bitzer Kuhlmaschinenbau Gmbh||Shaft mounted counterweight, method and scroll compressor incorporating same|
|US7993117||17 Jan 2008||9 Aug 2011||Bitzer Scroll Inc.||Scroll compressor and baffle for same|
|US7997877||17 Jan 2008||16 Aug 2011||Bitzer Kuhlmaschinenbau Gmbh||Scroll compressor having standardized power strip|
|US8133043||14 Oct 2008||13 Mar 2012||Bitzer Scroll, Inc.||Suction duct and scroll compressor incorporating same|
|US8142175||17 Jan 2008||27 Mar 2012||Bitzer Scroll Inc.||Mounting base and scroll compressor incorporating same|
|US8152500||17 Jan 2008||10 Apr 2012||Bitzer Scroll Inc.||Scroll compressor build assembly|
|US8167595||1 May 2012||Bitzer Scroll Inc.||Inlet screen and scroll compressor incorporating same|
|US8328543||3 Apr 2009||11 Dec 2012||Bitzer Kuehlmaschinenbau Gmbh||Contoured check valve disc and scroll compressor incorporating same|
|US8342795||1 Jan 2013||Emerson Climate Technologies, Inc.||Support member for optimizing dynamic load distribution and attenuating vibration|
|US8641392||10 May 2011||4 Feb 2014||Bitzer Kuehlmaschinenbau Gmbh||Scroll compressor bodies with scroll tip seals and extended thrust region|
|US8672654||17 May 2011||18 Mar 2014||Bitzer Kuhlmaschinenbau Gmbh||Shaft mounted counterweight, method and scroll compressor incorporating same|
|US20070243082 *||13 Apr 2006||18 Oct 2007||Gene Fields||Sealed compressor with structure on lower housing shell to assist weld placement|
|US20090185921 *||23 Jul 2009||Bitzer Scroll Inc.||Scroll Compressor Having Standardized Power Strip|
|US20090185926 *||23 Jul 2009||Bitzer Scroll Inc.||Scroll Compressor and Baffle for Same|
|US20090185927 *||23 Jul 2009||Bitzer Scroll Inc.||Key Coupling and Scroll Compressor Incorporating Same|
|US20090185928 *||23 Jul 2009||Bitzer Scroll Inc.||Scroll Compressor Suction Flow Path & Bearing Arrangement Features|
|US20090185929 *||23 Jul 2009||Bitzer Scroll Inc.||Mounting Base and Scroll Compressor Incorporating Same|
|US20090185930 *||23 Jul 2009||Bitzer Scroll Inc.||Scroll Compressor with Housing Shell Location|
|US20090185932 *||23 Jul 2009||Bitzer Scroll Inc.||Scroll Compressor Build Assembly|
|US20090185933 *||23 Jul 2009||Bitzer Scroll Inc.||Non Symmetrical Key Coupling Contact and Scroll Compressor Having Same|
|US20090185934 *||23 Jul 2009||Bitzer Scroll Inc.||Scroll Compressor Bodies with Scroll Tip Seals and Extended Thrust Region|
|US20090269192 *||29 Oct 2009||Hodapp Thomas R||Support member for optimizing dynamic load distribution and attenuating vibration|
|US20100092319 *||14 Oct 2008||15 Apr 2010||Bitzer Scroll Inc.||Suction Duct and Scroll Compressor Incorporating Same|
|US20100092320 *||14 Oct 2008||15 Apr 2010||Bitzer Scroll Inc.||Inlet Screen and Scroll Compressor Incorporating Same|
|US20100254842 *||3 Apr 2009||7 Oct 2010||Bitzer Scroll, Inc.||Contoured Check Valve Disc and Scroll Compressor Incorporating Same|
|Cooperative Classification||F04C23/008, F04C2230/603, F04C2230/60|
|19 Aug 2002||AS||Assignment|
|21 Jun 2007||FPAY||Fee payment|
Year of fee payment: 4
|16 May 2011||FPAY||Fee payment|
Year of fee payment: 8
|4 Sep 2015||REMI||Maintenance fee reminder mailed|